Spinning machine for the -production of cocoons



J. PlNcHoN 3,118,270

SPINNING MACHINE FOR THE PRODUCTION OF cOcOoNs, OOPS AND PIRNs Jan. 2l, 1964 12 Sheets-Sheet 1 Filed Dec. l2, 1961 @2l-LM@ /ATTOVLNGLAE Jan. 21, 1964 J. PlNcHoN 3,118,270

SPINNING MACHINE FOR THE PRODUCTION OF COCOONS, COPS AND PIRNS u INVENTQR;

J. PlNcHoN 3,118,270

SPINNING MACHINE FOR THE PRODUCTION OF oOcOoNs, cOPs AND PIRNs y Jan. 21, 1964 12 Sheets-Sheet 3 Filed Deo. 12, 1961 Jan. 21, 1964 J. PlNcHoN SPINNING MACHINE FOR THE; PRODUCTION OF cOcOoNs, coPs ANO PIRNs l2 Sheets-Sheet 4 Filed Deo. l2, 1961 NvEN-mrl: j. PncfrOf? a wia-19A* ATTQELNESS J. PlNcHoN 3,118,270

SPINNING MACHINE FOR THE-PRODUCTION oF cocooNs, cops AND PIRNS Jan. 21, 1964 l2 Sheets-Sheet 5 Filed Dec. l2, 1961 H n O m ,n ENI m I W pI 0M L MIN M N mm EN Nm, mi@

ATTO'LNESE Jan. 21, 1964 J. PlNcHoN 3,118,270

SPINNING MACHINE: FOR THE PRODUCTION oF cocooNs, CoPs AND PIRNs Filed Deo. l2, 1961 12 Sheets-Sheet 6 Jan. 21, 1964 .1. PlNcHoN 3,118,270

SPINNING MACHINE FOR THE PRODUCTION OF COCOONS, COPS AND PIRNS Filed Deo. l2, 1961 l2 Sheets-Sheet '7 NVENTOR;

J. PINCHON Jan. 21, 1964 SPINNING MACHINE FOR THE PRODUCTION OF COCOONS, COPS AND PIRNS l2 Sheets-Sheet 8 Filed Dec. 12, 1961 J. PlNcl-loN 3,118,270

SPINNING MACHINE FOR THE PRODUCTION oF cocooNs, cops AND PIRNs Jan. 21, 1964 l2 Sheets-Sheet 9 Filed Dec. l2, 1961 EL 14'9 @in '152 INvENTolI;

j. Pme/70D @s Jan. 21, 1964 J. PlNcHoN 3,118,270

SPINNING MACHINE FOR THE PRODUCTION OF COCOONS, COPS AND PIRNS Filed Dec. 12, 1961 12 Sheets-Sheet lO Jan. 21, 1964 J. PINcHoN 3,118,270

SPINNING MACHINE FOR THE PRODUCTION OF COCOONS, COPS AND PIRNS Fild Deo. l2, 1961 12 Sheets-Sheet 1l C *f M ATTQRNEHS J. PINCHON 3,118,270

SPINNING MACHINE: FOR THE PRODUCTION oF cocooNs, Cops AND PIRNs 12 sheets-sheet 12 Jan. 21, 1964 Filed Dec. 12, 1961 E l E ws @mmm NQ bw Nm N\ i In i I m.\N\

MTW QN @l \N A\.\ .Nw/1 ,MW

1 AWGN-FOR: j, PCHC/vof? las ATTQLLN E55 United States Patent .lean inchon, 131 Blvd. de Mulhouse, Roubaix, Nord,

France, assigner otono-third to Fierre Diliies, Croix,

Nord, France, and one-third to Gerard Lemaire, Rouhais', Nord, France Filed Dee. 12, 196i, Sar. No. 153,773 Slaims priority, application France Sec. 15, 196i? 17 Claims. (Sl. l-t) To obtain cocoons, cops or pirns usable, for example, in weaving looms, use was hitherto made of installations comprising a carding machine followed by a divider and a rubber, a drawing frame, a mule for putting the yarn into the form of a solid of revolution (pirn), which can then be handled, and finally' another mule on which a plurality of the pirns produced by the preceding -winding operation are grouped in the form of cocoons or cops.

This method has a cer-tain number of disadvantages, more particularly; defects in the uniformity of the product and losses of material owing to the numerous handling operations necessary at the different stages of production; `a large labour force and considerable investment in respeelt to equipment and premises to house the equipment.

if it is desired to perform the above-mentioned operations successively by disposing machines in series one after the other, the result would be unsuccessful because the outputs of the machines are not the same and continuous operation is rendered difcult owing to numerous yarn breakages. Moreover, the conventional spinning system does not lend itself to this.

ln present-day installations, moreover, it is not possible to increase the speed of cards, sincev the rubber would then no longer have any time -to perform its work Satisfactorily.

The object of the invention is `to provide a high-output machine which is intended to be disposed yafter a card with a divider and rubber and in which the operations of twisting, drawing, spinning and Winding are eliec'ted continuously and automatically without `the intervention of any labour, without handling at the diiiererrt stages of production, and without any :loss of material. Furthermore, the machine is of very reduced size and enables the rubber disposed after the card to be reduced in size, so that production can be increased as a result of a possible increase in the carding speed. Finally, the machine irnparts a considerable false twist to the yarn, this false twist increasing its strength without obstructing the subsequent weaving operations, during which this false twist disappears.

The spinning machine for the production of windings, such as cocoons, cops or pirns according to the invention comprises a plurality of units each of which comprises a rotary and preferably horizontal spindle and a coaxial ring, at a speed of rotation proportion-al to that of the card, and is intended to receive a roving coming from the rubber, in order to produce a corresponding winding.

According to a further feature or" the invention, each ring contains a lateral eye serving` as a yarn guide and is rotated positively at a speed slightly diiierent from that of the spindle, while advance means ensure a periodic axial displacement or" the spindle with respect to the ring, the amplitude of this displacement being in turn axially offset, at each step, as the cocoon formation progresses.

in one embodiment, the means for rotating each ringl are so designed and arranged as to rotate the said ring at a speed such that me difference between the speed or" the ring and that of the spindle be inversely proportional to the diameter of the winding at the region where the yarn is being wound at any moment.

The invention also relates to installations comprising a Eil? Patented Jan. 2l, 1954 card with a divider and rubber feeding a cocoon producing machine as defined hereinbefore.

@ther features of the invention `will be apparent from the following description ,and the accompanying dra-wings which illustrate by way of example without any limiting force one embodiment of a spinning machine for the production of cocoons according to the invention.

ln the drawings:

FIG. l is a side View of the complete installation comprising a card with a divider and rubber followed by a cocoon producing machine according to the invention.

PEG. 2 is a corresponding plan view.

FlG. 3 is a front view in the direction of the arrow lll in FIG. 1l.

FlG. 4 is a diagrammatic longitudinal section showing the drive for the spindle rails and spindle extraction bars or the cocoonproducing machine.

FiG. 5 is a corresponding front View of FIG. 4.

FIG. 6 is a section substantially onthe line Vl-Vl in FIG. 2, to a larger scale.

FlG. 7 is a section on 'the line Vil-Vil in FIG. 6.

PEG. 8 is a diagram showing the complete installation for the control of the spindle bush holders and of the spindle extraction bars.

FlG. 9 is a larger-scale view of the winding stock shown in the bottom right-hand part of FlG. l.

FIG. l() is a plan view corresponding to FIG. 9.

PIG. ll is a larger-scale view of a partial section on the line Xl-Xl in FIG. l0.

FIG. l2 shows a detail or" FIG. 9 to a larger scale.

FlG. 13 is a horizontal section on the line Xlll-Xlll in FIG. 12.

FlGS. 14 and l5 are partial sections respectively on the lines XlV-XlV and XV-XV in FIG. 12.

FlG. 16 is a vertical cross-section on the line XVI- XVI in FlG. l2, to a larger scale.

FlGS. 17, l and 19 are vertical cross-sections respectively on the lines XVil-XVIL XVIl-XJlll, and XlX-EHX in FiG. 9.

FlG. 2t) shows the structure of the successive layers of a cocoon.

2l shows the configuration of the completed cocoon and FIG. 22 shows the starting stage of a new cocoon.

The installation shown in FIGS. l to 3 comprises a cardin.U macln'ne l, a divider 2, a condenser rubber 3, and a machine 4 intended to spin the slivers or rovings emerging from the rubber 3 and to forni cocoons with the resulting yarns.

Neither the carding machine l nor the divider 2 has any special features, although the condenser nubber 3 may be reduced in size in comparison with conventional rubbers, and ythe spinning machine for the production of the cocoons d is enti-rely novel.

The spinninG machine for the production of cocoons 4 comprises a frame with two cheeks l1 and `l2 formed by continuations of `the cheeks l and le of the rubber 3, said cheeks being braced by bars such `as l5 (see also PlGS. 4 and 6), of which four are provided, one above the other, in the embodiment illustrated.

The bars l5, which lare each formed by an assembly of -two b-ars l, i7 (FIG. 6), carry a double .bearing i3, 19, which in this example is a needle bearing, on the aXis of each sliver leaving the rubber 3.

The .rotary ring 2l (see also FIG. 22) is mounted in each double bearing, such as l2?, 19. There are thereyfore four lines of rings disposed at `four llevels formed respectively by the four bars l5 which constitute the ring carriers. Each rotary ring 2l has a hole 27 ifor the passage or the sliver to be spun, and is provided with a yarn cutter formed by an axial cutting blade 29, the

free end of which is level with the cylindrical surface of the completed cocoon.

Moreover, each ring carries a gearwheel 22 (FIGS. 6 and 7) substantially in the middle of its length. Two gear-wheels 22 associated with two `adjacent rings simultaneously mesh with an intermediate gearwheel 23 mounted loosely on `an axle 242-, preferably by means of a ball or needle bearing 25, the yaxles 2li being formed by screws which rat the same time serve as connecting elements for the two bars 16, 17. Other screws 2d serve to complete the assembly of the two bars.

Rotation of the rings is eifected by means `of a geanvheel 31 meshing lwith the iirst gearwheel 22 of the irst ring of the corresponding level. The gearwheel 31 is connected to a shaft 32 which rotates in the ring carrier and which carries a bevel gear 33 (-see also (EEG. 2) meshing with another bevel gear 34 connected to one of the ends of a shaft 3S rotating in the cheek 12 and carrying a chain wheel 66.

The chain 37 (FlG. l) or a belt, such as a V-belt, which takes its movement from la wheel or pulley 33 of 4an output shaft 39 (FIGS. l and 2) of a change-speed device V1 fixed on the vframe of the machine and provided with a manual control wheel 42, passes over the wheels, such as 36 `of the driveshaft of the rings of each of the fou-r levels.

Thus the change-speed device V1 simultaneously drives all the rings of the machine at the same angular speed.

The input shaft of the speed varying device Vl is shown at 41 and is driven by a motor MV at variable speed, which yis fed by the generator G of `a Ward-Leonard set GL, the three-phase driving motor of which is denoted by MT. The inductors of the `generator G are fed 4from a tachometric generator GT (FlG. l) driven by the card driving motor MC through the medium of ,an amplifier A controlled by a potentiometer lD which will be referred to hereinafter.

A rotary bush, such as 51, is disposed opposite each rotary ring 21 (FlG. 6) and coaxially therewith. Each bush 51 is also mounted rotatably in a double needle bearing 52, 53 is a spindle carrier 54 which is in turn formed by two bars S, 56, the ends or which are iixed in carriages such as 57 (FIG. 3) movable over a dovetail guide 53 connected to a baseplate 59 lined to the corresponding cheek 11 or 12 of the machine.

A spindle 61 (FIG. 6) is mounted slidably in each bush 51 and is connected thereto as regards rotation by means of a screw 62 mounted radially in the said bush, the end of said screw being engaged in a longitudinal slot 63 in the said spindle.

The heel of each spindle 61 carries two collars 64, 65 engaging on either side of a bar 6e referred to as the spindle extraction bar, which can move parallel to itself, also on dovetail guides 58, so as to cause the spindles to slide axially in the bushes. There is therefore a spindle extraction bar per spindle level.

Each spindle bush is rotated by a gearwheel 71 ('ElG. 6) connected to the said bush, the gearwheels of two adjacent bushes simultaneously meshing with another intermediate gearwheel 72 mounted loosely on an axle 75 xed in the spindle holder 54. The axles 73 are again formed by screws which at the same time serve to connect the bars 55 and 56.

The iirst bush of each spindle holder carries a wheel 81 (FIG. 3) over which passes a chain S2 which also passes over a wheel 83 connected to a shaft @il carrying a pulley 84. A common belt S5 passes over the four pulleys 84 of the four spindle levels and also passes over a pulley S mounted on the output shaft 87 of another changespeed device V2. The belt 85 also passes over a reversing pulley 3S (FIG. 3).

The input shaft 91 of the change-speed device V2 (FG. 3) is driven from the following elements: a pulley 92 mounted on the said shalt 91, a belt 93 passing over the pulley 92 and over a pulley mounted on a shaft l 95, a dog clutch 259 subiect to the action of a spring 261, a shaft 264 disposed in a pitY $6, a reversin box @7 (see also FlGS. l and 2), a belt 98 and the electric motor MC which at the same time serves to drive the carding machine through a belt 1&1.

Reference 1h22 (FIGS. l to 3) denotes the handwheel for adjustment of the output speed of the change-speed device V2.

The speed of rotation of the spindles is therefore proportional to that of the motor MC, i.e. to the speed of trie card, with adjustment possible by means of the change-speed device VZ.

The reciprocating movement of the spindle holders 54 is ellected by means of a baclcshaft scroll cable lll (PlGS. 4-6) which on each level passes over two loose pulleys 112, respectively mounted on axles 11d, 115, over two top pulleys 116, 117, and over a driving pulley 118 connected to a transverse output shaft 11@ of a winding stock mechanism, which is denoted generally by reference 121 (FlGS. l to 3) and which is disposed beneath the two change-speed devices V1 and V2.

A spindle holder drive cable 111 is provided at each of the two ends of the spindle holders. For this purpose, the shaft 119 extends over the entire width of the machine and carries a pulley 11S at each of its ends.

Moreover, each spindle extraction 'oar 66 (FIG. 6) is displaced in parallel relationship to itself by means of a system of two racks 125 connected respectively to the two ends of the said bar and each engaging with a corresponding gearwheel 126 connected to the corresponding shaft 114. It should be noted that the pulleys 112 over Wi ich pass the cables 111 for the backshaft scrolls for the drive of the spindle holders, which are already mounted on said shafts, are loose thereon. The manner in which the shafts 114 are rotated will be described hereinbelow.

The function of the winding stock 121 is to ensure axial displacements of the spindle bush holders.

It comprises a frame 131 (FIGS. 9 and 1G) with bearings 132 in which the shaft 119 rotates (see also FlG. 17).

Two brackets 134, 135 (FIG. 9) are xed on the baseplate 131 and support a plate 136, the bottom surface of which forms a dovetail guide 137 (FIG. 17), on which a carriage 133 slides.

The shaft 139 rotates in the carriage 13S and is connected to a worm 142 meshing with a worm gear 143 connected to the winding stock output shaft 119. A gearwheel 14d is also xed on the shaft 119 and meshes with a rack 145 connected to a rule 146 adapted to side longitudinally on the top of the baseplate 131. The opposite end of the rule 146 to the rack 145 carries a heel 147 (FGS. l2, 14 and l5), of which the longitudinal position on the rule 146 can be adjusted. To this end, the heel 147 can slide in a longitudinal mortis-e 151 ol' the rule and has a guide tongue 152 engaging in a slot 149 of the rule. A loclring screw 14rd mounted in the heel 147 and passing through the slot 149 in the rule enables the said heel to be locked in any desired relative position with respect to the rule.

The carriage 133 is reciprocated on its guide by means ol a transmission device comprising a shaft 15S (FIGS. 9 and l0) which constitutes the winding stock input shaft, a sleeve 155 (see also FlGS. l2 and 13) slidably mounted on the fluted end 157 of shaft 155'. Sleeve 156 is provided with dogs which are adapted to engage matching dogs on the hub 15S of a chain wheel 159. The device further includes a chain 161, another chain wheel leZ mounted on a shaft 163 which shaft is supported at one end in bearings 1li/5, (FlG. 9). The bearings are connected by means of supports 1645 and 1&7 respectively, to the frame 131 ot the winding stoclr. The other end of shaft le?, is supported in a casing 1653 which Vis supported on the top surface of the xed plate 13d. A drum cam 171 is connected to the shaft 163 and has a helical slot 172 in which engages a roller 173 (FIG. 17) mounted in the inner race of a ball bearing 174. The outer race of ball bearing 17d is housed in the transverse bore of an axle 175. The axle 175 is lxed in the top ends of two levers 175 and 177 (see also FlG. 9) respectively, and can slide in two horizontal grooves 173, 179 formed longitudinally in the side walls of the casing 16S.

The bottom ends of the two levers 176, 177 have longitudinal apertures E51, 182 respectively, in which are engaged the two ends of a spindle 183 which transversely passes through the carriage 138 in a hole 1G59 in the latter.

The two levers 176 and 177 pivot on an intermediate xle 155 which passes through two longitudinalV apertures and 137 in these two levers respectively. The axle e also passes through two vertical apertures 153, 139 lormed in the two vertical side walls of the casing 16S, and throughV .vo oblique slots 192, 193 formed in a forked end of a rule 19d which can slide longitudinally in a groove 195 (FGS. 9, 10, l1, 17, 18, 19) formed in the top face of the plate 135..

The longitudinal slidingV movement of the rule 194 is obtained by means of a screw 281 (PEG-S. 9 and ll), one end of which is mounted ina bronze ring-2h12 mounted a vertical wall of the support 167 while the otl er end is mounted in a part 223 fixed on the plate 1.36 by a screw The rotary movement of tr e screw 291 is obtained by means of a lon@toothedk gearwheel 225 connected to the screw 2t1 and meshing with a gearwheel 2536 connected to the shaft 139 carrying the worm 142, the latter being rotatable by various means which are described hereibelow.

The screw 2%1 may also undergo a slight movement of axial translation in its supports and it is urged into the position shown in the drawings by means of a spring 257 (FEG. 11) which bears against one end of the bearring and against a collar 22S of the screw 2in1.

A ratchet wheel 212 is fixed on an extension 211 (PEG. 18) of the ,vorm 142 and with it c2c-operates a pawl 213 mounted on an axle 2145 which is in turn rncunte a support 215 pivoting on the shaft 211. A spring urges the pawl into its position of engage.n ment with the ratchet wheel 212. The case 215 carries a finger 217 (see als Fl'G. 19) which slides alonf7 a cam 213 iixed on the top part of an angle-iron which is inl turn fixed on the winding stock baseplate 131.

On each rec rocating movement of the carriage 133 the catch 217 slides along the cam 218 against which it re ains applied under the action of the weig t of the case 215, and a spng (EEG. 19), and it terefore causes the ratchet wheel 212 to advance by means of e pawl 213, by one or more teeth (in the direction of e arrow f1 (Fl-G. 18)), while at the same time driving the 142 through the same angle.

A finger 221 for arresting the pawl 213 is fixed in a groove in the form of an arc of a circle coaxial with the ratchet wheel 212-, said groove being formed support 223 (FIG. 9) connected to the carriage 133. his arresting finger is so adjusted that when the case 215 arrying the pawl occupies its lowest position the said lnger keeps the pawl raised and free of the teeth of the ratchet 212 so that the latter can then beturned in the direction of the. arrow f2 (FIG. 18).

The intermittent low-amplitude angular movement of the ratchet wheel 212 is therefore transmitted on the one hand to the worm 142, displacing the location of the travel of the rack o, and on the other hand to the shaft 139 and the gearwheel 235, thus producing intermittent rotation of the screw 291 and anadvance of the rule 194.

The screw 142 may, however, be driven in the other direction continuously at a much more rapid speed by means of the hub 227 of the gearwheel 25.325, which is provided with dogs 223 which, under certain conditions d in 216 which will be. described hereinbelow, can engage with matching dogs 229 on the hub 15d (FIG. 13), this hub having to be. moved to thc left (in FlG. 13) so that it is disengaged from the hub 15S of the chain wheel 159.

The hub 156 is urged to move to the left under the action of a spring 231 against which it is kept engaged against the hub 155 by means of a releasable locking device controlled by a lever 232 (FlGS. v9, 12 and 16).

The lever 232 is a double lever mounted by means of an axle 233 in two supports 234, 235 connected to the winding stock baseplate 131. The bottom end of the lever 232 carries a spindle 236 provided with a roller 237 rolling on the top surface of the heel 147 of the rule 145.

The two ends of the axle 233 are kept applied resiliently downwards in the two supports 2.34, 235 by push-members 23S- 239 urged by springs 241, 242 subject to the action of adjusting screws 243, 2M mounted in caps 245, 246 respectively xed on said suoports;

Two catches 251, 252 (see also FIG. 13) connected to the lever 232 engage in an annular central groove 255 of the sleeve 156 and enable the latter to slide on the tinted shaft 157.

In the position illustrated, the lever 232 is slightly inclined upwards and to the right (FIGS. 9 and 12) so that the roller 237 resting on the heel 147 prevents the said lever from pivoting in the anticlockwise direction f3 under the action or the spring 231. After the heel 147 has escaped to the left beneath the roller 237, for reasons indicated hereinbelow, the lever 232 then pivots in the direction f3. It is returned in the opposite direction by the axial sliding movement of the screw 221, which is terminated by a stop formed by an adjusting screw 253 which is intended to push the top end of the said lever 232 in the direction of the arrow f4 (FIGS. 9 and l2).

Furthermore, the slider of the potentiometer PE, which is assumed to be rectilinear and which is connected to the shaft 133 (PEG. 9) in such manner that when the lever 177 occupies a substantially vertical position the supply voltage for the motor MV (FlG. 1) is at a minimum while when the said lever reaches its mam'nium inclination (in the direction shown in FlG. 9), the said voltage becomes maximum.

The winding stock input shaft 155 is driven by a transmission comprising the followin7 elements: a pulley 255 (Fl-G. 3) fixed on the shaft `155, a belt 256 which passes over the pulley 255 and over a pulley 257 (see also FlG. 2) fixed on a shaft 253 also housed in the pit 96, a dog clutch 262 urged by a spring 25d, a shaft 2d3, a reversing box 265, a chain drive 265 (see also FlG. l), a gear train 267e, 267i), 267e, 267d, 267e, 267i, a shaft 263-, a bevel gear 26912, 26915, a gear train 2795i, 2,7%, a chain drive 274 which takes its movement from the shaft 275 of the card 1, which is in turn driven bythe chain 101 from the motor MC.

The speed of rotation of the input shaft 155 of the winding stock 121 is therefore proportional to the speed of the motor MC, i.e. the speed ofthe card, and at the same time to that of the divider l2, the lments of which are driven by a gear train 28th, 23%, 280C, Zild, 2tle, 254.?, taking its movement from the gear 267b which forms part of the winding stock drive kinematic chain.

It was stated herenbefore that the spindle extraction bar Vo6 at each of the four levels is driven by two racks meshing with gearwheels 126 connected to a transverse shaft r111i (FlG. 6). FIG. 4 shows the four shafts 114;'- driving the four spindle extraction bars o6 of he four levels.

A sprocket wheel 271 is fixed on each of the four shafts 11d and an endless chain 272 passes over these four sprockets. On the two intermediate shafts 11dthe chain is kept in contact with the corresponding sprockets 271 by means of two pressure rollers 273.

Rotation of' the four shafts 114 is effected from the top shaft on which is xed a gearwheel 276 meshing with a gearwheel 277 which in turn meshes with another gearwheel Z755 fixed on a shaft K2.79, this shaft being referred to as the winch shaft because it carries a drum 232 on which a cable 233 for the suspension of a counterweight Seis wound.

The winch shaft 279 may be driven from two different sources of movement, namely: an electric motor with a reduction gear me and the output shaft 119 of the winding stock 121.

The transmission connecting the motor me to the winch shaft 279 contains a clutch 28S, preferably of the electromagnetic type. 'Ehe transmission between the winch shaft 279 and the winding stock output shaft 119 comprises the following elements: a clutch 236, also preferably of the electromagnetic type, a gearwheel 237, another gearwheel 28S meshing with the gearwheel 2.37 and a chain transmission 289 comprising two chain wheels 291 and 292 respectively fixed on the shaft of the gearwheel 238 and on the Winch shaft 279.

During operation of the machine, the extraction bars follow the movements of the spindle rails Se under the action of the transmission driven by the winding stock output shaft under the control of the clutch 2do, while when .the cocoons are doffed the extraction bars are actuated now by the counterweight 2.84, now by the motor me under the control of the clutch 285, under the conditions described in detail hereinafter.

The dog clutches 259 and 262 enable the drive connections for the spindles and .the winding stock to be broken when it is required to remove the spinning machine from the rubber 3, for example for repairs and maintenance, such as cleaning of the carding machine. To this end, the divider and rubber, and the spinning machine, are installed on cast-iron baseplates and can be shifted by any appropriate means, such as jacks and racks (not shown).

The operation of the complete spinning machine for the production of cocoons is as follows:

Assuming, in the first instance, that the machine is in working order and that the permanent state of operation has been established. The slivers leaving the rubber 3 are each spun by a unit consisting of a spindle, such las 61, and a ring, such as 21 (FlGS. 2 and 6). The spindles and rings are rotated by the devices described hereinbefore and at relative speeds which will be discussed in detail hereinafter.

The continuous rotation of the input shaft S of the widening stock 121 (FiGS. l and 9) induces a reciprocating rotary movement in one direction and in the other direction of the output shaft 11?, which actuates the back scrolls for the am'al displacement of the bush holders 54, and the transmission of a corresponding axial displacement of the extraction bars e6 through drives already described with reference to FiG. 4.

The reciprocating movement `of the bush holders varies in amplitude and location as the cocoon formation progresses. At the vbeginning of the formation of a cocoon (HG. the travel a of the spindles has to be small, and then it increases progressively until the cocoon reaches its maximum diameter d2, whereupon the amplitude b of the displacement remains constant but the location of the travel shifts towards the final pointed end of the cocoon.

ff the kinematics of the winding stock (FlG. 9) are studied in detail, it will be seen that the continuous rotation of the input shaft 155 is transmitted through the chain 151 to the top shaft 153 which therefore drives the cam 171 at constant speed. rfhe helical groove 172 in this cam is invariable, so the axle 175 moves horizontally with a reciprocating movement of constant travel bot as regards amplitude and location.

At the beginning of the formation of a cocoon, the rule 1% occupies the position shown in FlGS. 9 and 11, so that the axle 13S occupies its lowest position in the bottom end of the oblique groove 192 of the ruler 194. The

amplitude of the angular movement of the levers 177, 17o is therefore at la minimum about the axle 18S under the action of the cam 172 so that the axle 183, which is captive in the bottom aperture of these levers, describes its minimum amplitude travel. The carriage 13S therefore describes a minimum amplitude travel and the worm 142 carried by said carriage then acts as a rack by pivoting the gearwheel 143 through an angle corresponding to the axial travel of the said worm 142, thus inducing a corresponding angular movement of the winding stock output shaft 119 and, hence, a travel of corresponding length and location for the spindles on which the cocoons are formed.

On each movement of the winding stock carriage 133, the pawl Z13 under the action of the finger 217 sliding on the ramp 213 (FIGS. 18 and 19), causes the ratchet wheel 212 to pivot through a corresponding angle in the direction of the arrow f1, so that on each reciprocating movement the worm 142 pivots through a certain angle about its axis. On each reciprocating movement the gearwheel 143 is therefore offset angularly and induces a corresponding offset in the longitudinal location of the spindles. Since the rings occupy a fixed axial position, the successive layers of the formation of the cocoons therefore progress axially.

According to FIG. 20, however, it will be seen that until the maximum diameter d2 of the cocoon has been achieved the axial length of the turns must increase from the lengt a to the length b. This result is obtained because the rotation of the worm 142 under the action of the pawl induces corresponding pivoting of the `screw 201 through the gearwheels 205 and 205. The rule 194 meshing with the screw 201 therefore advances gradually to the right (FIGS. ll and 9) so that under the action of the ramp formed by the inclined wall 192r of the groove of the rule 194 the axle lS rises in the vertical slots 18S, 189 of the fixed casing 163 of the Winding stock; the bottom lever arm of the levers 176, 177, i.e. the distance between the axle 185 and the axle 183, increases progressively, while the top lever arm, i.e. the `distance between the axles and 185, decreases progressively.

Since the travel of the ame 175 in the horizontal slots of the casing 168 is constant, the horizontal travel of the carriage 138 increases progressively. The axial travel of the spindles therefore increases in the same proportion.

At a certain time, the axle 1go' will reach the level of the top surface of the rule 194. As from then on, -it will remain at the same level and rest on this surface irrespective of the length by which the rule 194 continues to move to the right under the effect of the rotary movement of the screw 201 driven angularly through a `certain angle on each movement of the carriage 138. As from that moment, the length o-f the reciprocating lmovement of the spindles is constant but continues to be oiset towards the final end of the cocoon by the action of the pawl which still turns the worm 142 through ya certain angle on each movement.

Moreover, it will be seen that the speed of rotation of the rings (though smaller than that of the spindles) is all the higher, the more the axle 183 (FIG. 9) has moved to the right from its vertical position, as a result of the control of the speed of the motor MV by the potentiometer PD, i.e. is all the higher as the yarn 2S winds over a smaller diameter of the cocoon. Once the diameter d?. (FIG. 20) has been reached, the minimum speed of the rings on each reciprocation cycle of the cocoons no longer varies.

The rule 146, which is disposed on the winding stock baseplate 131 (FG. 9) is also subject to a geometrically similar reciprocating movement to that of the spindles and the location of its travel moves progressively to the left whenever the carriage 138 effects its travel.

During all this time the roller 237 (FIG. l2) rolled on the top surface `of the rule 146 and held the sleeve 156 in engagement with the chain wheel 159 against the force of the spring 231i (see also FIG. 13), so that the Winding stoel; input shaft continued -to be connected to the drive of the cam 171 by the drive chain 161 of the top shaft 163.

'.[lhere will be a time, however, when the right-hand end of the heel lil? connected to the rule 14o escapes to the left beneath the roller 237. At that tirne, since the rule M6 occupied its extreme leftJhand position possible, the carriage 136 occupied its extreme right position, and the sarne applies to the coupling sleeve 227 as shown in broken lines in FIG. l2, at 227e. In consequence, when the roller no -loncer rests on the rule 146 the spring 221 abruptly pivots the lever 232 in the `anticloclof/ise direction, ic. in the direction of the arrow f3 (FIG. l2), and the coupling sleeve 156 abruptly released from the chain wheel S is now in engagement with the sleeve 227 by means of the dogs 229 and 22S.

rThe shaft 155, which continues to turn, therefore no longer drives the top shaft 163 for the reciprocating drive but now drives the sleeve 227, the gearwheel 2%, the shaft E139 and the worm 142.

This movement is not prevented by the pawl 213 because at this time the latter is retained by lche linger 221 (FlG. i9) in a position away from the teeth of the ratchet wheel 212, which now turns in the `direction of the arrow f2.

he carriage 138 is locked by the reciprocating drive, so that the rotation of the worm E42 induces a corresponding rotation of the output shaft 119 of the winding stoel-1. This rotation has a number of results:

(a) it returns the rack 145 and the rule E46 into the initial posi- `on, thus bringing the heel 147 beneath the relier 237 of the lever 232, the axle 233 .of which lifts slightly in its supports against the springs 241, M2.

(b) The rotation of te gear Wheel 26e meshing with the l ng gear wheel Zik? produces a rotation of the screw Zil in the Opposite direction or its previous intermittent rotation, so that the rule 194 is brought to its initial position and the axle 135 bears against the nose i325 (FIG. ll) of the rule 1624, the latter no longer being able to continue its reverse move-rient because of the relative position of the slots i3d-S9 (FIG. 17) and ld- 137' of the levers lic-i177 (FIG. 17). Towards the end of this movement, the screw 2ll bearing against the rule 9d compresses the spring 2-@7 while the stop screw 253 connected to the screw 213i pushes back the top end of the lever 232 (FlG. l2), Ten* resumes its initial position while consequently disengaging the direct drive of the worm and re-engaging +he reciprocating movement ne carriage i3d; the slots ld-137 or me ievers i ter with the si t l?, of the rule and the axle descends again along the vertical slots (Fi-G. l7) towards the bottom of the slot E52 of the rule l i which is urged to resume its position under the action ot the spring Ztl? which acts upc-n it tlrough the screw 291;.

All the components have therefore resumed their startposiion for a new cycle.

(c) During the return of the different elements or the WL ding st ci; to their 'i the spindles on wir ch the coco-ons were formed also retreat to their initial position for the formation or the cocoons while completely passing through rines, eg. 2l (PEG. 2l).

The sequence of operations during clotting will be exyarn 28 being Wound in a few turns of large pitch on the outer surface of the cocoon.

in the course or" this movement, during which the cornpleted cocoon passes through the ring, the bush holder passes over the Contact D (HG. 8). The contact C had been tensioned at the erfl of the formation cycle. in consequence, the clutch ac (FIGS. 4 and 8) is released while the c ch Z' is engaged. The motor me is stopped, so that the spindle extraction bar 66 is locked While the bush holder Sd co res its travel slightly and pushes the cocoon in front of it on the spindle nl. The time-switch Min is tensioned. The bush holder passes over its electric Contact D, thus indu ng release of the clutch 23S, the countervveight returns the spindle extraction bar 66 to a position ag Ast the bush holder :lso that the spindle el advances in its bush il while driving the cocoon 3d with it, the said cocoon consequently moving away from the bush end formation cone When the time to which the time-sw; ch Mn has been set expires, the clutch 2do engages so that the spindle continues to advance with its bush under the action of the winding stock input shaft M9. The yarn begins to fi/'ind on the now released formation cone at a finer pit .i than the pitch on the outer surface of the cocoon, since the standard reciprocating movement produced by the winding stock has now been resumed and at the moment the pitch changes the knife engages the yarn and cuts it. Winding oi the yarn is continued on tue formation cone 69.

Actuation of the nressbutton A (FIG. S11-alternatively an automatic contact could be provided-results in operation of the motor and reduction gear me, engagement of the clutch ZSS and release of the clutch 2%. The counterweight riseswhile the spindle retreats cornpletely to the right in FlG. 6) so that its free end is retracted inside the bash e2. The cocoons, which are no longer held, then drop on the grids (HG. 3) inclined towards the cheel; il which is suitably aperture/i to enable the cocoons to be coiiected from these grids. The spindle extraction bar 5% actuates the Contact B (PEG. 8), this inducing release of the clutch 235 and tensioning of the time switch Min. The counterweight 2t descends again ant brings the spin-:lle heel ed back against the bush holder When the time to which the time switch has been set expires, the clutch 286 is reengaged while the clutch 285 remains released. The normal cocoon torn -on cycle recomneices.

During formation of the cocoons, e bush holders and sp die extraction bars are f iven together positively in their re i caring from the output of the win-fi stock lZl by means of the beit and the clutch a .s and the transmission 2,57, 2%,

sie 2id, 239, Q32, 2F73, 277, 27o, ld respectively. Enr g this time the counterweiglit scends and descends permanently under no-load condihons.

The spindle heels elif, on the other hand, are driven alone, by the action of the counterweigh 2da in one direction and by the motor and reduction gear me the other direction (said motor at the same time bringing the counterweight up), by means of the transmission containing the clutch To sum up, generally, all the in producing machine 3 are subgect to t card i. The speed of rotation or the s dies is proportional to that oi the card ive motor MC, with the possibility of manuel adjustment by means of wheel 1162 of the change-sneed device V2. The speed or the elements of th winding stoel: 221 which controls the reciprocation cycle of the spindies is also proportional to that of the motor MC, and iinally the speed or" rotation of the rines is also proportional to the speed or tie motor MC with automatic variation (under the control of the winding stock El), in dependence on the instantaneous diameter of the cocoons with the possibility of manual adjustment by means of the wheel of the change-speed device Vi.

ie speed of the ln these conditions, the characteristics of the yarn and of the resultant cocoons are determined positively and precisely. siivers or rovings leaving the rubber undergo determined drawing and twisting without the need for conventional operations such as handling and successive unwinding operations which are so liable to cause yarn positive rotation of the spindles and of the rings enables the yarns to be given any desired characteristics. Twisting has a favourable effect on the compacto-ess of the cocoon and enables a higher drawing rate to ce used.

The diameter of the cocoons is determined by the xed earn l (FlG. i8) so that by modifying the proiile of this the 'num diameter the cocoons can be i aried.

The crossing (winding pitch of the yarn ou the cocoon) can be adjusted 'oy inlluencing the Aspeed or" the input 155 of the winding stock lll, for example by replacing the gearwhcel 255 (PEG. 3) by another of different diarneter.

it should be noted that each revolution of the spindles gives one twist turn and that each revolution of the rings with respect to the spindles corresponds to one winding turn and one supplementary twist turn, which disappears on subsequent unwinding ot the cocoon, because this is really a false twist w? ch considerably increases the strength of t le yarn during production and which does not obstruct -he subsequent weaving operations since it disappears then.

The invention is naturally not limited to the embodinient described and illustrated, winch has been given by way of example without any limiting force, and numerous rnodilioations familiar to those versed in the art may be made thereto, without thereby departing from the scope of the invention.

l claim:

l. A spinning machine for the production ol windings, such as cocoons, cops. and pirns, intended to be disposed after a card having a divider and la condenser rubber, said machine comprising ya plurality of spinning units, each oi which comprises a rotary spindle rotating `at a speed propoi-tional to that of the card, and a coaxial ring rotating at a speed gradua ly diering fr said spinale resp-onse to the actual diameter of the cocoon being formed, said spinning unit being intended to receive a roving leaving the condenser rubber, in order to form a corresponding winding.

2. A spinning machine Iaccording to claim 1, wherein each ring comprises a lateral eye serving as a yarn guide, and wherein ring Vrotating means positively rotates said ring at ia speed slight `diderent from that of fthe spindle, while advance means ensure periodic axial displacement of the spindle with respect to the ring, the amplitude of said displacement being in turn axially oiset, on each step, as the winding formation progresses.

3. A spinning macmne as defined in claim 1, wherein each ring has a lateral eye serving yas .a yarn guide, and wherein ring rotating means positively rotates said ring at a speed slightly `different from that of the spindle, Whe advance rneans ensure periodic axial displacement of the spindle with respect to the ring, the amplitude o the iirst layers of yarn on the spindle increasing progressively so 4as to `give the conical starting shape, whereupon the ainplitude remains constant until completion of the formation of the cocoon, while remaining a ially odset on each cycle,

4. A spinning machine according to claim l, wherein drive means for `the rotation of each ring are adapted to rotate said ring yat a speed such that the didere-nee between the speed of the ring and that of the spindle be inversely proportional to the diameter of the cocoon at the regi n where the yarn is being wound at eac i moment.

5. A spinning machine for the production of cocco-ns, cops zand pirns, intended to be disposed after a card hav ing a divider and a condenser rubber, said machine com- 4m the rotational speed ofV psing a plurality of spinning units, each of which cornprises a rotary spindle slidably mounted in a bush and rotating at a speed proportional to that of the card, and a coaxial ring, said spinning unit be-ing intended to receive a roving leaving the condenser rubber, in order to form a corresponding cocoon, one end of said bush being conical to serve as a formation cone for fthe beginning of the cocoon.

6. A spinning machine according to claim 5, wherein each spindle bush carries a gearwheel and the gear-wheels or all the bushes are connected together.

7. A spiraling machine tor the production of cocoons, cops and pinos, intended to be disposed after a card ha"- ing a divider and a condenser rubber, said machine cornprising a pair of parallel guides, `a spindle rail the two ends of which slide on said parallel guides, `a series oi spindle holder bushes mounted in said spindle rai-l, a rotary spindle mounted in each of said spindle holder Xbushes and rotating at a speed proportional to that of the card, a spindle extraction bar, the two ends of which are adapted to slide on said parallel guida, each spindle having a heel axially connected to said spindle extraction bar, a ring rail the two ends of which rest on ysaid parallel guides respectively, rings carried by said ring rail coaxia ly with said spindle respectively and rotating at ya speed slightly greater than that of the corresponding spindle, each ring forming together with the corresponding spindle a spinning unit intended to receive a roving leaving the condenser rubber, in order to form a corresponding cocoon, and means for reciprocating said spindle rail on said 'guides to insure periodical axial displacement of said spindles with respect to said rings, the amplitude or" said displacement being in turn axially olset on each step yas the coco-on vformation progresse-s.

8. A spinning machine according to claim 7, wherein said spindle extraction bar is driven with ya reciprocating movement in the direction of the laxes of the spndles, in synchronisrn with the .aidal reciprocating movement oi said spindle rail under the action of the same driving means.

9. A spinning machine according to claim 7, wherein power means, and an appropriate transmission, enable the spindle extraction bar to be retracted in order to withdraw the spindles into the bushes and free the cocoons, while further power means, enable the spindles to be returned to their initial position with respect to the bushes.

l0. A spinning machine for the production of cocoons, cops and pirns, intended to be disposed after a card having a divider rand `a condenser rubber, said -rnaohine comprising a plurality of spinning units, each of which cornprises a rotary spindle rotating at a speed proportional to that of the card, a coaxial ring, said spinning unit being intended to receive a roving leaving the condenser rubber, in order to form `a corresponding cocoon, and means for driving the spindles with an reciprocating movement, said driving means comprising a winding stock which comprises an input shaft, a -rocldng lever having a variable lever ar-m actuated by said input shaft, `a reciprocating carriage actu-ated by said rocking lever, a longitudinal yworm carried by the said carriage and operating as a rack meshing with an output gearsvheel connected to a shaft, said shaft being the bacleshaht scroll shaft, which controls the reciprocating vmovement of the spindles, and a pawl system adapted angularly to oit-set the worm on each movement of the carriage.

ll` A spinning machine accordin7 to clahn l0, wherein said winding stock further comprises cam means, to vary fthe lever arm of the roer: g f ever in response to the anguiar oi'tset movement of the worm.

l2. A spinning machine according to claim ll, wherein a device vfor controlllng the end of the cylc, and driven by a rack meshing with a pinion connected to the back- 13. A spinning machine according to clairn 10, further comprising a drive systern for rotation of the rings which comprises a variable speed ytno-tor controlled by a potentiometer connected to said varia le lever arrn.

i4. A spinning machine according to claim 13, wherein said variable speed motor is fed by the generator of a Ward-Leonard set, the inductors of which lare fed from a taclioineuic generator driven by he card through an arnplirier controlled by said potentiometer.

15. A spinning machine for the production of cocoons cops and pirns, intended to be disposed after a card having a divider and a condenser rubber, said machine cornprising la pair of parallel guides, a spindle rail the two ends of which slide on said parallel guides, `a series of spindle holder bushes mounted in said spindle rail, a rotary spindle mounted in each of said spindle holder bushes and rotating at a speed proportional to that of the card, a spindle extraction bar, the two ends of which are adapted to slide on said parallel guides, each spindle having a heel axially connected to said spindle extraction bar, a ring rail the two ends of which rest on said parallel guides respectively, ings carried by said ring rail coaxially with said spindles respectively and rotating at a speed slightly greater than that of the corresponding spindle, each ring forming together with the corresponding spindle a spinning urit intended to receive a roving leaving the condenser rubber, in order to forrn `a correspondinT cocoon, means for reciprocating said spindle rail on said guides to insure periodical axial displacement of said spindles with respect to said rings, the amplitude of said displacement being fin turn axial-ly offset on each step as the cocoon formation prog'esses, means for axially displacing the spindle holder bushes and the spindles so as to pass each completed cocoon rapidly through the ring to aiiect doiing of |the cocoons, means for temporarily retaining the spindles axially during this movement so as to uncover formation cones so that the yarns begin to wind at the normal pitch, means for withdrawing the spindle bushes and the spindles, the 'latter by Ia slightly greater amount than the spindle bushes for retracting the spindles into the bushes in order to drop the cocoons, and nleans for returning the spindles into the position -for the formation of the cocoons which have been begun on the for-mation cones.

16. A spinning machine according to claim 15, wherein each ring is provided with a yarn cutter formed by la blade extending in a direction parallel to the axis of said ring and tangential to the completed cocoon, so as tocut the yarn at the moment the pitch changes when the yarn passes from the rapid pitch on the surface of the cornpleted cocoon to the line-pitch formation cone.

17. Installation for the production of cocoons, cops and pirns, from a fibrous textile material adapted to be introduced ilto a card, said installation comprising a card with a divider and a condenser rubber, and a spinning machine disposed after said rubber and comprising a plurality of spinning units each of which comprises a rotary spindle rotating at `a speed proportional to that of the card and a coaxial ring rotating -at a speed gradually differing from the rotational speed of said spindle in response .to the actual diameter of the cocoon being formed, said spinning unit being intended to receive a roving leaving the `condenser rubber, in order to form a correspon( inf7 cocoon.

References Cited in the file of this patent UNITED STATES PATENTS 774,744r Draper Nov. 15, 1904 1,127,994 Hill et al. Feb. 9, 1915 2,142,111 Camp Ian. 3, 1939 2,778,136 Luttgen et al Ian. 22, i957 2,995,902 Leach etal Aug. 8, i961 

1. A SPINNING MACHINE FOR THE PRODUCTION OF WINDINGS, SUCH AS COCOONS, COPS AND PIRNS, INTENDED TO BE DISPOSED AFTER A CARD HAVING A DIVIDER AND A CONDENSER RUBBER, SAID MACHINE COMPRISING A PLURALITY OF SPINNING UNITS, EACH OF WHICH COMPRISES A ROTARY SPINDLE ROTATING AT A SPEED PROPORTIONAL TO THAT OF THE CARD, AND A COAXIAL RING ROTATING AT A SPEED GRADUALLY DIFFERING FROM THE ROTATIONAL SPEED OF SAID SPINDLE IN RESPONSE TO THE ACTUAL DIAMETER OF THE MENT, A FIRST MEANS FOR ACTUATING THE OTHER OF SAID FORMING ELEMENTS, FOLDING MEANS AT SAID CARD FOLDING STATION COMPRISING BREAKER BLADES AND FOLDER ARMS FOR FOLDING OVER PORTIONS OF THE CARDS TO ENCLOSE THE POCKETS THEREOF, FOLD ARMS ENGAGEABLE WITH THE FOLDED OVER PORTIONS OF THE CARDS TO COMPLETE THE FOLDING OPERATION, A SECOND MEANS FOR OPERATING SAID BREAKER BLADES, A THIRD MEANS FOR OPERATING SAID FOLD ARMS, SAID FOLDER ARMS BEING ACTUATED BY SAID ACTUATED ELEMENT, SEALING ELECTRODES AT SAID CARD SEALING STATION, SAID ACTUATED ELEMENT BEING OPERATIVELY CONNECTED THEREWITH TO SIMULTANEOUSLY ENGAGE SAID ELECTRODES WITH OPPOSITE SIDES OF THE CARD, AND MEANS FOR SUPPLYING HIGH FREQUENCY CURRENT TO SAID ELECTRODES. 